Transmission



D. W. KELBEL TRANSMISSION 2 SHEETS-SHEET l Filed April '7, 1945 am, mw

A@ mw Nw l my mw m mM. Nm. MN N SN. mh MN :E v uw NN QN MN MN NN Nw 4 D, W. KELBEL Jan. 15, 1952 TRANSMISSION Filed April 7, 1945 2 SHEETS-SHEET 2 Patented Jan. 175, 1795i TRANSMISSION Donald-W; Kelbel; Muncie, Indi', assi'gliortoBorg#v Warner Corporation, Chicago;` Illi, a.` corpora-e' tion ofIllinois AppiicationApril 7, 1945, SeriaINQJSLN'S iofvolaiins; (C1. 74'-759 invention relatesto transmissions for; auto;-

motive vehicles andi more particularly to sucli transmissions`4 comprising planetary gearing,

Itis an object of my invention to provide an improved:transmission`- of this type providingf a plurality of speed ratiosv between.. the drivingl and drivenshafts andwhich is compact and is simple inl construction and which may be economically manufactured;

Itis afurther object to provide a transmission of'v thistype', comprising two clutches, each of whichlY has two engagingY positions,V with the clutches functioning tjo provide three different speed ratios, dependingv on the positioning of the clutches; It is contemplated that one speed,l ratioA shall be'provided'when both` clutches areV in a first 'engagingpositiom another speed ratio, shallbe' provided whenboth" clutches are in ar second engaging position and that still another speedratio shall be4 providedY when one clutch is in its'lirst engaging position andthe other clutchy isin its second engaging position.

Itis a more specic object' of my invention to' provider an improved planetary gear arrangement' which is compact and simple in construction and wliich is particularly suitableA for use" inV combination with the two clutchesabove mentionedfcrproviding a plurality of speedratios be?- tween the drive' and'driven shafts of'the` transmission:

The invention consists ofthe novel construetions,l arrangements and'r devicesV to be" hereinafter-described andclaimed for carrying out the above stated objects and such other objectsas will appear from the -following description of a certain preferred embodiment illustrated inthe accompanying drawings, wherein:

Fig. 1 is av longitudinal sectional'view" of a transmission embodying principles of the invention;

Fig. 2is a cross sectional view'takensubstan'- tiallyon thefline 2 2 of Fig. 1; and

Fig. 3 is a diagrammatic illustration of transmission shown in Fig. l.

Like vcharacters of reference designate like' parts in the several views.

Referring now to the drawings, the illustrated transmission comprises an input shaft Ill,` a clutch shaft II, an intermediate shaft IZfand a driven shaft it. The shaft IQ may be connected the' with an internal combustion type driving engine;

(not shown) for' anautomotive vehicle and'the shaft i3 may be connected with the driven' Wheels of 'the vehicle in which `the transmission is installed.' It will loe-noted thatfth'eshaft II pilates 1nthe. Sharrand that, the snaft' |213 isn piloted' in botlr thej'sh'aft" II and'in'f theslaft I3.' Aeentrifugalclutcli I14and`a frjee Wheeling clitfcir 55, are provided"V for: connecting' the shafts` rI'trf' andij I I A;H planetarygear "set'indicated"generally, at' i6, positive'typeclutches"IIandI8, apo'sitive. type brake l Sand-afriction'brake' 2o `are'jprovidedj f orteffectively connectingV theclutchfshafti Ijand the' driv'enshaft" I 3 in a plurality of *speed'jratios,I as Will be hereinafterf'describ'ed. 'v The centrifugal clutch' Iifj comprises' tire-usual ny.' Wheel" 2"I for an" internalk coniliustionr` enginei whichis connected'witlithe shaftl 0,' a" pressure plate2`2"; and a`4 driven clutcli"4 disc 23: The prese" sure'plate 22 isconnectedwiththe ily Wheel" 2| so" as tobe rotatable tlierewitlibyfn'rean's' offaclutcfh cover 2t'a bolted to the 'liywheelg studs' 25j' fixed; with"u respect" to the pressure` plate" 2:2i and ein'A tending thro-ugli?`'appropriat'el openings 'in ther covenand'ears" 2 2 frmedion "tliepressurdplate" 22 andlextending, through"suitable slotsL 24u pro; videdl inthe3 cover1'2lI4-f The `studsi 25j: areslid'ably disposedin their"openingsin'Y the cover y "tlfa the -pressure-plate=mayj move 'ftoward they Wheel" to `clamp the `clutch' di'scfZ -31;therebletvvle'en for-"ene"- gagingtheelutch'. Therclutelfdisc 23 is'xed to" is splined ltofthe shaft I I Y.

The lpressure" plate 22j isi moved"y toward thelyf nuts 3ii fitting witl'iiniL suitable openings" in j t e" coverl 24j anditl-reA nuts* liifmay beradjulsted" fori moving' the plate-23 itoward*or away-'from he' wheel '2 IL Springs 3 #aree-provided betvveen the?" sure plate 22am function @gnomi'the-plates 2 z`L and 28"apart` Th'ejplate ,2,8v and'i'the'weightsflj the connection between the plates by means of the studs 25 and 29, and as the speed of the shaft I increases, the weights 21 move outwardly. On such outward movementl of the weights, the lever portions 34 of the weights function to pry the plates 22 and 28 aart and to clamp the friction disc 23 between the pressure plate 22 and fly Wheel 2I to engage the clutch, as is apparent from an inspection of the form of the lever portions 34 as shown in the drawing. The movement of the plates 22 and 28 apart is in opposition to the action of the spring 32, and the reaction on the plate 28 is taken by the springs 3| between the plate and the cover 24. The clutch I4 is thus engaged to couple the shafts I0 and II upon the speed of the former shaft increasing sufficiently.

The one-Way clutch I5 comprises rollers 35 disposed between the hub 26 and a cylindrical portion 36 xed with respect to the shaft I0. The hub 26 and portion 36 are formed with cams (not shown) on their inner surfaces which are of such shape that the rollers 35 will not engage between the hub and cylindrical portion when a drive sfrom the shaft I9 to the driven shaft I I; however, the rollers 35 will engage if the shaft II is rotated in the forward direction while the shaft Ii] is not being driven. The overrunning clutch I5 thus assures a drive from the shaft II to the shaft I0 if the engine (not shown) for driving the shaft ID is inoperative.

The planetary gear set I6 comprises a sun gear 4I] formed on the shaft I2, pinions 4I in mesh with the sun gear 46, dual pinion units 42 comprising pinions 43 and 44, with the pinions 43 being in mesh with the pinions l I and a ring gear 45 in mesh with the pinions 43. The pinions 4I and pinion units 42 are rotatably disposed on shafts 46 and 41 respectively, and these shafts are fixed within a planet gear carrier 48. A sun gear 49 is in mesh with the pinion 44 and is under the control of brake as will appear.

The pinion carrier 48 is connected with a sleeve 56 rotatably disposed on the shaft I2, and the ring gear 45 is connected with a radial coupling flange 5I rotatably disposed on the sleeve 50. The carrier 48 is connectible through a one-way roller clutch 52 with a positive brake element 53. The clutch 52 comprises rollers 54 disposed between a cylindrical portion 48a of the carrier and the brake element 53, and suitable cams (not shown) are formed on the external surface of the brake element 53 so that when the latter element is held stationary, the rollers 54 engage to prevent a reverse rotation of the carrier 48. A friction brake element 55 is splined to the sun gear 49, as shown.

The clutch I1 is of the positive type and functions to connect the clutch shaft II with either the carrier 48 or the sun gear 40 of the planet gear 'set I6. The clutch I1 comprises a shiftable clutch element 60 splined to a cylindrical portion IIa of the clutch shaft II and provided with teeth 6I and 62. The shiftable element 60 is connected with a shift sleeve 63 by means of a pin 64 extending through the sleeve and into the shiftable element 60. A clutch element 65 having teeth 66 is splined to a sleeve portion 48h of the carrier 48, and a clutch element 61 having teeth 68 is splined to the intermediate shaft I2. The clutch I1 has two engaged positions, one in which the shiftable element 60 is shifted tovinterengage the teeth 62 and 66 and the other in which the shiftable element 60 is shifted to interengage the teeth 6I and 68, the element 60 being shown in the latter position of engagement. In the former position of the clutch 1, the clutch functions to couple the shaft II with the carrier 43. In the position in which it is illustrated, the clutch functions to couple the shaft I I with the shaft I2 and the sun gear 46. Blocker synchronizer mechanism 69 of known construction is provided for preventing a shifting of the shiftable element 30 until the parts to be coupled thereby are in synchronism.

The clutch I3 is quite similar in construction to the clutch I1. This clutch also has two engaged positions and in one of these positions it functions to connect the driven shaft I3 with the ring gear 45 and in its other position it functions to connect the shaft I3 with the carrier 48. The clutch I8 comprises a shiftable element 10 splined within a cylindrical portion I3a of the shaft I3. The shiftable element 1E] is provided with teeth 1I and 12, and a shift sleeve 13 disposed on the cylindrical portion I3a is connected by means of a pin 14 with the shiftable element 19 for moving the latter element. The sleeve 56 is provided with clutch teeth 15, and the flanged coupling element 5I is provided with clutch teeth 15. The clutch sleeve 15 in one engaged position has its teeth 12 interengaged with the teeth 15 to connect the sleeve 50 and thereby the carrier 48 with the driven shaft I3, and the clutch sleeve 13 in its other engaged position has its teeth 1I interengaged with the teeth 16 to couple the flanged coupling element 5I and thereby the ring gear 45 with the driven shaft I3, the shiftable element 15 being illustrated in the drawing in latter position. The clutch I8 comprises also blocker synchronizer mechanism 11 which is provided for preventing a shift of the shftable element 1o into either of its engaged positions until the parts to be coupled thereby are in synchronism.

The positive brake I9 comprises a shiftable sleeve 88 disposed within and splined to the transmission housing 8I. The sleeve 85 is provided with teeth B2 and 83, as shown. The brake element 53 is provided With teeth 34, and the ring gear 45 is provided with teeth 85. The sleeve 80 is adapted to be shifted to interengage the teeth 82 and 84 to condition the transmission for for- Ward drive, and the sleeve 83 is adapted to be shifted in the opposite direction to interengage the teeth 83 with the teeth 85 to condition the transmission for a reverse drive.

The friction brake 25 comprises a brake band 86 effective to engage the drum 55 and operated by any suitable operator indicated schematically at 81. The brake band 6B when effective brakes the drum 55 and thereby the sun gear 49 as is apparent, this brake being effective for second and overdrive speed ratios through the transmission, as will be hereinafter described.

In operation, the illustrated transmission provides low, intermediate, direct and overdrive speed ratios in forward drive and a reduced speed ratio in reverse drive. The shiftable element 89 of the brake I9 is shifted axially to the left in Fig. 1 interengaging the teeth 82 and 84 to condition the transmission for forward drive. Such engagement of the clutch I9 functions to hold the brake element 53 stationary so that the oneway clutch mechanism 52 functions thereafter as a one-way brake to prevent reverse rotation of the carrier 48 While allowing forward rotation of the carrier. For 10W speed ratio the shiftable clutch element 6I) of the clutch I1 is in the position in which it is illustrated with the teeth 6I and 68 interengaged. The shiftable clutch eleare in their said first engaged positions, another of said power trains being completed when both of said clutches are in their said second engaged positions and a third of said power trains being completed when one of said clutches is in its said first and the other of said clutches is in its said second engaged position, a brake for an element of said gear set for providing a reaction for those of said power trains having speed ratios other than one to one, and a one-way brake for another element of said gear set for providing another power train between said shafts when both of said clutches are engaged.

3. In power transmission mechanism, the combination of a drive shaft, a driven shaft, means for providing a plurality of power trains at diierent speed ratios between said shafts and including a direct drive, said means comprising a gear set and a pair of clutches, one of said clutches being adapted to connect said drive shaft with elements of said gear set and having rst and second engaged positions and the other of said clutches being adapted Yto connect said driven shaft with elements of said gear set and having first and second engaged positions, said clutches when both are engaged completing said power trains, one of said power trains being completed when both of said clutches are in their said first engaged positions, another of said power trains being completed when both of said clutches are in their said second engaged positions and a third of said power trains being completed when one of said clutches is in its said rst and the other of said clutches is in its said second engaged position, said clutches connecting said drive and driven shafts with the same element of said gear set to provide said direct drive, a brake for an element of said gear set for providing a reaction for the other of said power trains, and a one way brake for an element of said gear set for providing a low speed power train between said shafts and overrunning when said first named brake is engaged for providing the other` power trains between the shafts.

4. In power transmission mechanism, the combination of a drive shaft, a driven shaft, means for providing power trains at different speed ratios between said shafts and including a gear set and a pair of clutches, said gear set comprising a ring gear, a planet gear carrier, and a pair of sun gears, one of said clutches having first and second engaged positions for connecting said drive shaft either to one of said sun gears or to said planet gear carrier respectively, the other of said clutches having first and second engaged positions for connecting said driven shaft to either said ring gear or said planet gear carrier respectively, said clutches when both are engaged completing said power trains, one power train being completed when both clutchesare in their first engaged positions, another power train being completed when both clutches are in their second engaged positions and a third power train being completed when said first named clutch is in its second and the other clutch is in its rst engaged position, and a brake for the other of said sun gears for providing a reaction for those of said power trains having speed ratios other than one to one.

5. In power transmission mechanism, the combination of a drive shaft, a driven shaft, a planetary gear set for providing a power train between said shafts, said gear set including two planet gears in mesh with each other. a ring gear meshing with one of said planet gears and a sun gear meshing with the other of said planet gears, a planet gear portion connected with one of said first named planet gears, a sun gear in mesh with said last named planet gear portion, a carrier for said planet gears, means for connecting said carrier With said drive shaft, a, brake for said last named sun gear, means for connecting said first-named sun gear with said drive shaft, and means for connecting said ring gear with said driven shaft.

6. In power transmission mechanism, the combination of a drive shaft, a driven shaft, a planetary gear set for providing power trains of different speed ratios between said shafts, said gear set including two planet gears in mesh with each other, a ring gear meshing with one of said planet gears and a sun gear meshing with the other of said planet gears, a planet gear portion connected with one of said rst named planet gears, a, carrier for said planet gears, a sun gear in mesh with said last named planet gear portion, a brake for said last named sun gear to provide one speed ratio, means for connecting said carrier to said drive shaft to provide a second speech ratio, a brake for said carrier for providing another speed ratio, means for connecting said first-named sun gear with said drive shaft, and means for connecting said ring gear with said driven shaft.

7. In power transmission mechanism, the combination of a drive shaft, a driven shaft, a planetary gear set for providing a power train between said shafts, said gear set including two planet gears in mesh with each other, a ring gear meshing with one of said planet gears and a sun gear meshing with the other of said planet gears, a planet gear connected with one of said rst named planet gears, a carrier for said planet gears, a sun gear in mesh with said last named planet gear, a brake for said last named sun gear, means for connecting said ring gear with said driven shaft, and means for connecting said carrier with said drive shaft.

8. In power transmission mechanism, the combination of a drive shaft, a driven shaft, a planetary gear set for providing power trains of different speed ratios between said shafts, said gear set including two planet gears in mesh with each other, a ring gear meshing with one of said planet gears and a sun gear meshing with the other of said planet gears, a planet gear connected with one of said rst named planet gears, a carrier for said planet gears, a sun gear in mesh with said last named planet gear, a brake for said last named sun gear, a clutch having two engaged positions and connecting said drive shaft with either said carrier or said first named sun gear, and a clutch having two engaged positions and connecting said driven shaft with either said ring gear or said carrier.

9. In power transmission mechanism, the combination of a drive shaft, a driven shaft, a planetary gear set for providing power trains of different speed ratios between said shafts, said gear set including two planet gears in mesh with each other, a ring gear meshing with one of said planet gears and a sun gear meshing with the other of said planet gears, a planet gear connected with one of said first named planet gears, a carrier for said planet gears, a sun gear in mesh with said last named planet gear, a brake for said last named sun gear, a brake for said carrier, a clutch having two engaged positions and connecting said drive shaft with either said carrier or said rst named sun gear and a clutch having two engaged positions and connecting said driven shaft with either said ring gear or said carrier, said rst and second named clutches when connected respectively with said rst named sun gear and with said ring gear when said second named brake is engaged providing a low speed ratio and providing a higher speed ratio when said second named brake is engaged, said first and second named clutches when connected respectively with said carrier and with said ring gear when said second named brake is engaged providing an overdrive speed ratio.

10. In power transmission mechanism, the combination of a drive shaft, a driven shaft, a planetary gear set for providing gear trains of different speed ratios between said shafts, said gear set including two planet gears of the same size in mesh with each other, a ring gear meshing with one of said planet gears and a sun gear meshing with the other of said planet gears, a planet gear connected with one of said rst named planet gears and being larger than said rst named planet gear, a carrier for said planet gears, a sun gear in mesh with said last named planet gear, a brake for said last named sun gear, a one-way brake for said carrier, a positive type clutch having two engaged positions and connecting said drive shaft with either said car- 3f) rier or with said first named sun gear, and a positive type clutch having two engaged positions and connecting said driven shaft with either said ring gear or said carrier, said rst and second named clutches when engaged rey; spectively with said first named sun gear and 10 said ring gear providing a low speed power train through the transmission when said one-way brake is eective and providing an intermediate speed power train between said shafts when said first named brake is effective, said clutches when respectively connecting said drive shaft and said carrier and connecting said driven shaft and said ring gear providing an overdrive speed ratio between said shafts when said first named brake is engaged.

DONALD W. KELBEL.

REFERENCES CITED The following references are of record in the le of this patent:

UNITED STATES PATENTS Number Name Date 861,791 Anderson July 30, 1907 980,407 Clarke Jan. 3, 1911 2,005,726 Banker June 25, 1935 2,134,398 Cotterman Oct. 25, 1938 2,194,954 Ravigneaux Mar. 26, 1940 2,279,986 Griswold Apr. 14, 1942 2,293,358 Pollard Aug. 18, 1942 2,322,676 Vincent June 22, 1943 2,334,402 Flinn Nov. 16, 1943 2,381,786 Tyler Aug. 7, 1945 FOREIGN PATENTS Number Country Date 5,835 Great Britain Mar. 1, 1907 443,735 Great Britain Mar. 5, 1936 48,019 France Oct. 16, 1937 (Addition to No. 809,102)

439,886 France Apr. 19, 1912 

